Flying cut-off



FLYING CUT-OFF Filed Aug. 2D, 1964 4 Sheets-Sheet 5 INVENTOR. JOSEPH S. WALSH ATTORNEYS Filed Aug. 25, 1964 4 Sheets-Sheet 4 INVENTOR. JOSEPH S. WALSH 2 flM/YZQQQJWWZ? Ed 23l E 230 Q ATTORNEYS United St 3,301,115 FLYING CUT- EFF Joseph S. Walsh, Fairview Park, {lhio, assignor to The glider Company, Cleveland, 0115s, a corporation of Filed Aug. 25, 1964, Ser. No. 391,865 2i) illaims. (Cl. 83-31 This invention relates generally as indicated to a flying cut-off and more particularly to certain improvements in a flying cut-off of the type illustrated in my copending application, Serial No. 336,417, filed January 8, 1964, entitled Flying Cut-Off.

In such aforementioned copending application, there is disclosed a high energy cut-oil for severing travelling work in continuous strip processing lines, such as cold roll forming operations. Such cut-off is capable of extremely rapid cycling and yet is of an extremely simple and inexpensive construction not requiring expensive drive motors, shafts, clutches, and the like. A double edge cutting blade is mounted in a window frame for reciprocation back and forth through the work so that work severing occurs as the result of movement of the blade in either direction. The blade is powered by a high pressure piston-cylinder assembly which may be cocked at either extent of travel and released substantially explosively to drive the blade through the work. The blade is then latched and recocked on the opposite side of the work.

The blade is illustrated as mounted within the supporting frame for short distance movement with respect to the frame to permit the blade to travel with the work, hence to obtain a flying cut-oil. Tube gripping dies are also mounted closely adjacent the blade travel path on a special spring loaded carriage to grip the tube when the blade is triggered so that the travelling tube will carry the dies and blade a short distance therewith. While the cut-off machine illustrated in such copending application is of an extremely simple nature when compared with conven tional flying cut-off presses, the mounting of the dies in a separate travelling carriage as well as the mounting of the blade for work movement with respect to its support frame requires a complex and still fairly expensive construction.

It is accordingly a principal object of the present invention to provide certain improvements in the flying cutoff illustrated in the aforementioned copending applica tion making such cut-off of a still more simple and less expensive construction.

A further important object is the provision of a high energy high speed cut-oft which is mounted such that the tool, tool guides and dies may move resiliently a short distance with the work.

Another important object is the mounting of such cutoff by means of parallel suspension straps permitting the tool to travel a short distance with the work.

Yet another object is the provision of a cut-off mounted by means of parallel single leaf springs permitting resilient tool travel a short distance with the work.

A further object is the provision of simplified work gripping dies for use with such high energy cut-off.

A still further object is the provision of a more foolproof latch and trigger mechanism for latching and cocking the tool to be driven through the work when triggered at substantially explosive speeds.

Yet another object is the provision of such a high energy cut-off which can adjustably be mounted to attack the work from any desired angle.

Other objects and advantages of the present invention will become apparent as the following description proceeds.

To the accomplishment of the foregoing and related ends, the invention, then, comprises the features hereinafter fully described and particularly pointed out in the claims, the following description and the annexed drawings setting forth in detail certain illustrative embodiments of the invention, these being indicative, however, of but a few of the various ways in which the principle of the invention may be employed.

In said annexed drawings:

FIG. 1 is a side elevation partially broken away illustrating a cut-off in accordance with the present invention;

FIG. 2 is an end elevation partially broken away and in section of such cut-oil as seen from the left in FIG. 1;

FIG. 3 is a detail side elevation partially broken away and in section of the cutting mechanism including the cutting tool, tool actuator, guides, and work gripping dies;

FIG. 4 is a rear elevation of the cut-off as seen from the right in FIG. 1;

FIG. 5 is an enlarged detail elevation of one of the work gripping dies as seen from the line 55 of FIG. 2;

FIG. 6 is a section of the die taken substantially on the line 6-6 of FIG. 5;

FIG. 7 is an enlarged detail view of the latch and triggering mechanism employed with the present invention as seen from the line 7-7 of FIG. 2;

FIG. 8 is a horizontal section as seen from the line 88 of FIG. 7 showing such triggering mechanism;

FIG. 9 is a side elevation of a slightly modified form of the present invention wherein the cut-off may be tilted about the axis of the travelling work path to attack the work from any desired angle; and

FIG. 10 is a fragmentary section taken substantially on the line 1tl--lil of FIG. 9 illustrating the support for the cutting tool.

Referring now to the annexed drawings and more parcularly to FIGS. 1 through 3, the illustrated cut-off may be mounted on a base 1 comprising a flat plate-like structure 2 having downwardly offset feet 3 which may be secured to a further subbase structure or stand. Such stand may be mounted on rails or the like for movement into and out of the mill line. Although the illustrated cut-off is particularly well suited for use in high speed tube lines, it will be appreciated that with various shape blades, other rolled or extruded shapes may be severed with the present invention. Furthermore, the cut-off of the present invention may be employed to sever tubes or shapes manually fed thereto rather than those travelling therethrough in a high speed automatic line.

Mounted on the top of the plate 2 of the base 1 are parallel laterally spaced upstanding housing plates 4 and 5 having the profile shown more clearly in FIG. 1. As seen in FIG. 1, the profile of each plate includes vertically extending front and back edges 6 and 7, respectively, with the front edges being provided with deep rectangular recesses 8, aligned in each plate, for passage of the workpiece W therethrough. The top of each plate is provided with two inclined surfaces 9 and 10 with a horizontal intermediate surface 11 interposed therebetween.

Various structural members interconnect the plates 4 and 5 to provide a sturdy and rigid frame housing for the cut-off. With additional reference to FIG. 4, it will be seen that a vertically extending plate or web 13 interconnects the lower portions of the plates 4 and 5 and a horizontal plate 14 is welded on the top thereof. Horizontal plates 15 and 16 are welded between the upstanding frame plates 4 and at the rear of the cut-off and such further serve to support cylindrical air reservoirs 17 and 18. Such reservoirs thus are mounted between the plates and extend in a parallel vertical manner as shown in FIG. 4 to provide a compact assembly. At the top of the frame plates, a vertically extending plate 20 is secured therebetween and a top plate 21 is secured tothe vertical plate 20 and is supported on the horizontal surfaces 11 of the frame plates. At the front forward edge of the frame, a further horizontal member 22 extends between the plates. A rigid frame housing is thus provided for the cut-01f.

Referring now more particularly to FIGS. 1 and 2, an inner frame or support for the tool mechanism comprises laterally spaced side plates 25 and 26 which are of the wide U-shape profile shown in dotted lines in FIG. 1. Such plates are interconnected by a vertical plate or web 27 at the back thereof and by a fairly thick base plate 28 at the bottom. The legs of the plates 25 and 26 have horizontal blocks 30, 31, 32 and 33 secured to the inside faces thereof and clamping bolts 34, 35, 36 and 37 extend through such legs and into the blocks. Such bolts also pass through elongated vertical slots 38, 39, 40 and 41 as well as similar slots 42, 43, 44 and 45 in spacers or shims 46, 47, 48 and 49, respectively, secured to the inside faces of the plates 4 and 5 with the slots therein aligned with the slots in such plates.

When the clamping bolts are tightened, the interior frame comprised of the plates 25 and 26 is thus firmly secured to the exterior frame comprised of the plates 4 and 5 further rigidifying the frame structure. The elongated slots accommodating the clamping bolts through the plates 4 and 5 as well as the spacers 46 through 49 permit vertical adjustment of the interior frame with respect to the housing and such adjustment may be accomplished by a jack screw shown generally at 52 in FIG. 1.

Such jack includes a drive housing 53 mounted on the horizontal plate 14 which is secured between the plates 4 and 5 and rotation of a horizontal shaft 54 by means of a suitable tool projected through an aperture in the plates 4 or 5 will rotate jack screw 55 threaded in elongated nut 56 secured to the base 28 of the inner frame. Thus when the clamping bolts 34 through 37 are loosened, the vertical position of the inner frame may readily be adjusted to an extent permitted by the length of the slots 38 etc.

The inner frame 25, 26 is thus adjustably supported on the outer frame 4, 5 and such inner frame in turn supports the blade, blade guide, actuator and dies illustrated without such frames in FIG. 3. Such assembly, which may be termed generally the work severing or cut-off mechanism, includes a pneumatic piston-cylinder assembly 53 which is secured between a top retaining plate 59 and the uppermost shelf 60 of die supporting frame 61. The top retainer plate 59 is secured to the top shelf 60 of the frame 61 by tie rods 62 and 63 secured by nuts 64 to the top plate 59 and threaded in hubs 65 and 66 which are secured to the top shelf 60. The piston 68 of the assembly 58 is secured to piston rod 69 which projects through both ends of the cylinder 70 and the end projecting through the shelf 60 is secured at 71 to rectangular elongated frame 72 which has a window opening 73 therein.

As seen in FIG. 1, a double edge cutting blade B is removably supported in the frame 72 centrally of the opening 73 by removable clamping plates 75 and 76 held in place by recessed head screws 77 passing through the plates, blade and frame 72. The profile configuration and thickness of the blade may be that disclosed more particularly in the aforementioned copending application and such comprises generally oppositely directed reverse curve cutting edges which are symmetrical about the center of the blade and thus the center of the work passing through the machine in the direction of the arrow 79 seen in FIG. 2. In FIG. 1, the blade B is illustrated in a position passing through the work W severing the same.

Collars 80 and 81 may be secured to the frame 72 having bushings 82 therein which enclose guide rod 83 which extends from the top shelf 60 of the die supporting frame 61 to the bottom shelf 34. The upper end of the guide rod 83 may be threadedly secured in the hub 66 and the lower end may be secured to the bottom shelf by nut 85. A rod 36 parallel to the rod 83 also extends between the top and bottom shelves 60 and S4 of the die frame 61 and is secured to the bottom shelf 34 by nut 87 and is threaded in the hub 65 on the top of the upper shelf 60. The blade frame 72 may be guided along one or both of the rods 86 and 83 by means of such collars 80 and 81 and the bushings therein projecting from one or both sides of such frame. It can now be seen that actuation of the piston-cylinder assembly 58 will cause the frame 72 and thus the blade B to reciprocate back and forth along the guide rods extending between the upper and lower shelves of the tube gripping die frame 61.

The frame 61, which may, for example, be an aluminum casting, includes two struts or legs 90 and 91 extending parallel to each other between the upper and lower shelves which widen at the center to include hubs 92 and 93 supporting the work gripping dies therein. The struts 90 and 91 may each be provided with reenforcing edge flanges 94 as well as a horizontal web brace 95 and may be interconnected by plate 96 held to bosses 97 on the respective struts by fasteners 98. (See FIG. 3.)

Mounted on each strut 90 and 91 are pairs of latch assemblies 100 and 101 with such assemblies of each pair on each strut being horizontally aligned. Thus four in all latch assemblies are provided and such assemblies are shown in more detail in FIGS. 7 and 8. Such latch assemblies may be of a rotating dog type and cooperate with latching pins 102 and 103 which project through the frame 72 so that such frame will be held at each end of its stroke afforded by the actuating assembly 58. Such latch mechanisms will engage the pins 102 and 103 to secure the blade frame 72 at the opposite ends of its stroke and when pressure is built up within the cylinder 70 of the assembly 58, the latch will be triggered to cause the blade to be driven substantially explosively through the work between the work gripping dies supported by the hubs 92 and 93.

The work severing mechanism, which comprises the blade, blade guide, actuator and dies is supported from the inner frame by means of four parallel single leaf flat spring straps 105, 106, 107 and 108 of equal length, each of which is secured at its upper ends to the respective leg blocks 30 through 33 of the inner frame 25, 26 by suitable caps 109 with fasteners 110 passing therethrough and into the legs. The lower ends of each spring strap are secured in a similar manner to the upper and lower shelves 60 and 84 of the frame 61 by caps 112 with fasteners 113 passing therethrough and through the straps into the shelves. The straps 105 through 108 constitute resilient parallelogram spring supports for the cut-off mechanism permitting the same to travel a shont distance with the travelling work W as the blade B passes therethrough. Thus the entire cut-off mechanism is supported by the inner frame 25, 26 for short distance resilient movement with the work W as the severing action is obtained.

Referring now more particularly to FIGS. 2, 5 and 6, mounted within each of the hubs 92 and 93 of the struts 90 and 91 of the frame 61 are work gripping dies 115 and 116 which are allochirally identical in form and only the die 115 is shown in detail in FIGS. 5 and 6. A flanged liner 117 is mounted in the hub 92 with the flange 118 thereof being recessed within the face of such hub. A cylindrical die housing 119 is fitted within the liner 117 and is provided with a flange 120 extending over the face of the flange 118. Such flange 120 is provided with a plurality of recesses 121 illustrated as four in number in FIG. 5, having slots extending circumferentially in one edge thereof as indicated at 122 accommodating cap screws or like headed fasteners 123 which project therethrough and are threaded in the flange 118 of the liner 117. Also projecting through the flange are a plurality of set screws 124 having squared projecting tips 125 with lock nuts 126 mounted thereon. Such set screws extend through the flange 120 and bear against the flange 118 of the liner 117. The recesses 121 are quadrant spaced about the flange 120 as are the set screws 124 as well as the cap screws 123. It can now be seen that the die can readily be removed from the hub liner 117 simply by loosening the set screws 124 and then rotating the die in a clockwise direction as viewed in FIG. 5 to remove the shanks of the screws 123 into the recesses 121 and then axially pulling the die from the hub. Conversely, the die can readily be inserted into the hub by rotating the die in a counterclockwise direction to place the shanks of the screws 123 in the slots 122 and then tightening the set screws 124 locking the same in place.

The work gripping die itself is comprised of four collet members 130, 131, 132 and 133 having semi-circular recesses 134 in the edge faces thereof which accommodate cylindrical rubber or the like resilient spacer elements 135 therebetween. Such cylindrical spacer elements separate or tend to enlarge the circular opening formed by the collet members so that when the die is in a released position, a tubular workpiece or the like will pass readily therethrough. The collet assembly formed by the collet members through 133 and the spacer elements therebetween may be held in place by a set screw 137 threaded into a radially extending tapped aperture in the die housing 119. A shoulder 138 on the housing 119 may also be employed to secure the assembly against movement axially to the right as viewed in FIG. 6.

To actuate or open and close the collet assembly for gripping the tubular workpiece passing therethrough, a collet actuator 14%) is mounted within annular recess 142 in the die housing 119 with the axial outer flange 143 thereof being provided with a seal 144. The interior surface of such flange is provided with a wedge surface 145 which cooperates with a similar exterior surface on the collet assembly so that when the actuator 14*!) is moved axially to the right as seen in FIG. 6, the collet assembly will be contracted compressing the cylindrical elements 135 therebetween constricting the circular opening therethrough thus to grip a tubular workpiece passing therethrough. The actuator 149 is provided with an oppositely extending inwardly offset axial flange 146 which has a cylindrical inner surface flaring slightly as indicated at 147 to provide a workpiece guide through the die. An annular retainer plate 148 is secured to an end of the die housing 119 by suitable fasteners 149 and such retainer encloses the axial flange 146 of the actuator 140 and a sliding seal 151) is provided therein to provide an expansible sealed chamber 151 between the retainer, the housing 119, and the actuator 1411. A radially extending air passage 152 having a tapped outlet 153 is provided leading to such chamber.

It can now be seen that air pressure supplied through the port 153 to the chamber 151 will cause the actuator 141) to move axially to the right as seen in FIG. 6 contracting the collet assembly to grip a tubular workpiece passing through the die. When the air pressure is released, the cylindrical resilient elements interposed between the collet elements will cause the collet assembly to expand forcing the actuator to the left due to the wedge surfaces between the actuator and the collet members. In this manner, an extremely simplified quick acting workpiece gripping die is provided which can readily be removed and replaced with different dies for workpieces of varying sizes and configurations. The die sup- 6 ported in the hub 13 will be allochirally identical to that shown in FIG. 6.

Since the cut-off of the illustrated invention may be required to operate at speeds obtaining in excess of 100 cuts per minute, it will be appreciated that a foolproof and positive latching mechanism which can be released instantaneously in response to a work length signal is required. One form of latch mechanism which has been found to meet the above requirements is that illustrated in FIGS. 7 and 8. The strut 30 on which one of the latches 1111 is mounted is provided with a mounting block having a semi-circular recess 161 therein extending transversely of the direction of travel of the frame 72. A cap 162 secured to the block 161! by suitable elongated tie bolts 163 is also provided with a semi-circular recess 164 mating with the recess 161 and securing in the circular aperture formed thereby the shank portion 165 of the latch operating mechanism which includes rotatable circular latch members 166 and 167 on the opposite ends thereof.

The circular latch member 167 includes a peripheral recess 169 into which a stop member 170 projects which is fastened to the cap 162. The latch member 167 is also provided with a wedge shape notch 172 into which latching dog 173 snugly seats. The circular latch memher 166 on the opposite end of the shank 165 is provided with a circumferential recess 175, the end 176 of which is shown in engagement with the pin 103 projecting from the frame 72. A pin 177 projects from the latch member 167 and tension spring 178 extends therefrom to pin 17? which is the L-shape lower projecting end of screw 1811 adjustably mounted in block 181 secured on the top of the block 166 and the cap 162. The tension provided by the spring 178 can thus be closely controlled by adjusting the screw and locking the same in place with lock nuts 182.

The latching dog 173 is mounted in a channel 184 in the block 166 which is covered by the leg 185 of angle bracket 186 which is fastened to the block 160 by suitable fasteners 18?. The dog 173 is mounted on rod 138 of piston 189 housed within cylinder 190. The cylinder 1% is mounted on a support plate 191 secured to the block 161 and the bracket 186, and a heavy duty compression spring 192 is housed within the cylinder extending between the piston and the blind end thereof. The rod end of the cylinder is provided with passages having tapped outlets 194 and 195 so that such end may be pressurized and vented to extend and retract the rod and thus the latching dog 173. Pressure supplied to the piston will remove the same to the left as seen in FIG. 7 compressing the spring 132 to remove the dog 173 from the notch 172 in the circular latching member 167. Conversely, relief of the pressure within the cylinder will permit the heavy duty spring 192 to drive the piston and thus the dog to the right as seen in FIG. 7 into latching position.

With the parts in the positions shown in FIGS. 7 and 8, the frame 72 will be latched in its lower position with the pin 1113 being engaged by the surface 1'76 of the circular latch member 166. The dog 173 will be projected into the notch 172 to hold the parts in a static condition. At this time, pressure is built up within the actuating cylinder 70 which will tend to drive the blade B upwardly through the work. However, because of the latching mechanism, the blade will be held in its cocked position. Upon a suitable work length signal, air pressure will be supplied to the blind end of the piston-cylinder assembly 189, to retract the dog 173 from the notch 172 permitting the latch members 166 and 167 to rotate about their axis. Such latch members will rotate in a counterclockwise direction as viewed in FIG. 7 releasing the pin 103 and thus the frame 72 permitting the blade to be driven substantially explosively through the work.

The pin 177 will then move over center holding the latch mechanism with the surface 200 of the peripheral recess 169 in engagement with the stop 170. This will also move the surface 201 of the recess 175 through substantially 90 to be positioned in a substantially horizontal plane to be engaged by the pin 103 when the blade is shot back through the work. In such condition, the spring 192 will be pressing the dog 193 against the latch member 167 but it will not enter the notch 172 until the pin 103 engages the surface 201 to rotate the latch members 166 and 167 in a clockwise direction to align the notch with the dog permitting the same to snap therewIthin. The recesses 175 and 169 in the latch members 166 and 167, respectively, extend peripherally approximately 90 and are 45 offset from each other. The over center spring 178 will hold the latch mechanism in the prcpr position to be reset by the engagement of the pin 103 with the surface 201. It will be understood that allochirally identical in form latches will be provided on each side of the frame 72 to engage the opposite ends of the projecting pin 103 to hold the blade support at each end of its stroke.

It can now be seen that there is provided a substantially foolproof latching mechanism which will provide positive cocking of the blade at each end of the stroke travel and such which is capable of operating instantaneously permitting extremely rapid cycling of the cut-off,

Referring now to FIGS. 1, 3 and 4, the reservoirs 17 and 18 in the housing 4, 5 may be supplied with air under pressure from conduits 210 and 211 indicated in FIG. 4 and one reservoir may be supplied with air under relatively high pressures, such as on the order of from about 500 to about 1000 pounds per square inch. The other reservoir may be supplied with air at somewhat lower pressure and the reservoirs 17 and 18 may then be termed low and high pressure reservoirs, respectively. Such reservoirs are connected by conduits 212 and 213 to low and high pressure valves 214 and 215, respectively, mounted on the shelf 21 extending between the side plates 4,. 5. Such valves may be three-way valves and the valve 214 may supply the low pressure from the reservoir 17 to line 216 or line 217, which are connected to shuttle valves 218 and 219, respectively. Similarly, the valve 215 will supply the high pressure from reservoir 18 to line 220 or line 221 also connected to the respective shuttle valves. Such shuttle valves are mounted at the opposite end of the cylinder 70 of the assembly 58 and each are provided with a shuttle which will move back and forth depending upon the position of the valves 214 and 215.

OPERATION The operation of the cut-off will be substantially the same as that described in the aforementioned copending application. With the cutting blade in either its up or down position and latched in place by the latches 100 or 101, the directional valve 215 will be operated to supply high pressure air from the reservoir 18 to the proper end of the cylinder 70. For example, if the frame 72 is in its lowermost position with the latches 101 engaging the pin 103 to hold the same in a cocked position, the valve 215 will be set to supply high pressure air to line 221 through the shuttle valve 219 to the bottom or lower end of the cylinder 70. Extremely high pressure will then be built up on the lower side of the piston 68 tending to drive the piston and thus the rod as well as the frame 72 and blade B held thereby in an upward direction. The blade in such cocked position will, of course, be clear of the work passing through the dies and the frame opening 73. With the workpiece W, illustrated in the form of a tube, thus passing through the dies 115 and 116, the cut end of the tube will trip a flag or other tube length sensing apparatus to energize the trigger circuits which will supply air under pressure to the rod end of the piston-cylinder assemblies of the latches 101 pulling the dog 173 from the notch 172. When the latches 101 are thus released,

the high pressure built up on the lower ide of the piston 68 will drive the blade B upwardly at a substantially explosive force and the air within cylinder 70 will be exhausted through ports 223 in collar 224 which surrounds the mid-portion of the cylinder 70 of the assembly 58. As the piston 68 reaches the mid portion of its stroke as illustrated in FIG. 3 with the blade B having entered the WOIk W as indicated in FIG. 1, limit or preferably proximity switching will now shift the valves 214 and 215 with the former now supplying low pressure air through the conduits 212 and 216 to the shuttle valve 218 to supply low pressure to the upper end of the cylinder 70 to act as an air brake slowing the blade frame 72 to a stop as the pins 102 move behind the latches 100. The latches are such that when kicked they will keep the blade from returning and yet permit a slight overtravel of the frame 72. When the latches are firmly engaged, the valves 214 and 215 will again be actuated with the valve 215 now supplying high pressure air through the conduit 220 to the top of the cylinder 70 through the shuttle valve 218. However, the air pressure exerting the force on the piston 68 will not drive the blade back through the tube until the tube length signal triggers the latches 100.

When the latches 100 are released, the blade will then fly back through the work with the air within cylinder 70 being exhausted through the ports 223 and at the midpoint of travel. The valves 214 and 215 will then be actuated with the latter being closed and the former supplying low pressure air now through the conduit 217 and the shuttle valve 219 to the bottom of the cylinder 70 to act as a brake or retardant as the blade frame 72 is driven into engagement with the latches 101. At the same time that the latches are released by the triggering circuits, supplying air to the piston-cylinder assemblies 189, 190, such air may also be supplied to the ports 153 of the dies causing the die actuators 140 to move axially compressing the collet assembly so that the workpiece W will be gripped thereby as the blade moves therebetween. The dies will be actuated only momentarily and when gripping the workpiece W with the blade B passing through such workpiece therebetween, the entire actuating assembly will move a short distance with the work, such being permitted by the single leaf spring straps 105 through 108 supporting the assemblies within the frame housings.

FIG. 9 EMBODIMENT It will be understood that in the severing of circular elongated travelling work such as tubing, the blade may enter the work at any angle transversely thereof and still not result in an unbalanced loading on the symmetrical blade edges. However, there are many tubular and nontubular rolled shapes which should not be attacked from a vertical direction to obtain the best severing action. For example, a rectangular section tube should be attacked from a direction which will bisect a corner angle thereof. In this manner, the cutting points on the opposite sides of the blade will be maintained chordally opposite each other and a balanced loading will result on the cutting bl ade. Moreover, a better severing action is obtained with the blade passing in a direction at an angle to the wall of the rolled shape. In conventional out-0E presses, due to the heavy and massive nature thereof, it is not always possible to adjust the cut-01f to attack the work at the desired angle. Lateral shifting of the blade may be obtained by complex mechanisms shifting the blade sideways as the press head descends. Such horizontal components of the blade movement then do not permit the vertical movement of the press head to be utilized to its fullest extent to perform the severing action.

Since the cut-off of the present invention is of an extremely simplified nature and is relatively light weight, not employing heavy drive motors, press heads, platens, clutches, brakes and the like, it is then readily possible to mount the cut-off for tilting movement about the pass line so that the blade may attack the work from any desired angle. One such form of cut-off adjustment is shown in FIGS. 9 and 10. A base 1, identical in form to that shown in FIGS. 1 and 2, may be employed having a top platform or plate 2 with vertically offset feet 3. Similarly, such base may be mounted on a carriage for movement into and out of a mill line. From the platform or plate 2, a pair of laterally spaced vertically upstanding plates 230 and 231 are provided with arcuate top rails 232 and 233. Such upstanding plates may be joined by webs or other horizontal framing vertically to rigidify the same. The base 1 having the plates 230 and 231 on the top thereof with the arcuate rails may then comprise the fixed base of the cut-off.

The cut-off is mounted in a housing comprising laterally spaced plates 234 and 235, the lower edge of each being provided with an arcuate rail as shown at 236 and 237, which are supported on the arcuate rails of the fixed base plates 230 and 231, respectively. Gibs 238 and 239 are mounted on the plates 234 and 235 enclosing the rails 232 and 233 of the fixed base plates and yet permitting arcuate adjustment of the frame 234, 235 with respect to the fixed base. The arcuate rails 232, 23 3, 236 and 237, as well as the gibs 238 and 239 may have the center of the pass indicated at 240 as their centers so that the blade points will always pass through such pass center regardless of the adjustment of the housing 234, 235. Such adjustment may be obtained by any of a variety of mechanisms such as a circular rack and pinion, a circular rack and worm, hydraulic motor means, etc. Also, suitable clamping mechanisms may be provided firmly to secure the movable and fixed portions of the housing together once the desired angle of attack is obtained. For convenience in obtaining the desired angle, a scale and pointer may be provided, respectively, on the fixed and movable housings. It will, of course, be understood that by extension of the arcuate rails, the cutting tool can quickly be shifted from a vertical to a horizontal position. Thus the cutting tool may be readily adjusted to attack the work from any angle.

The housing plates 234 and 235 correspond structurally to the plates 4 and 5 in the FIG. 2 embodiment and the cut-off mechanism will be mounted with respect to such plates in substantially the same manner as shown in FIG. 2. The single leaf spring straps 165 through 108 may be of such rigidity properly resiliently to support the cutting mechanism which is of relatively light weight in either the horizontal or vertical position of the tool. If desired, laminated leaf springs may be employed.

It can now be seen that there is provided a light weight simplified cut-off for elongated travelling work such as tubular product, which due to such simplified nature, can be mounted in its entirety for short distance movement with the work. It will, however, be appreciated that such movement may be obtained by an accelerator mechanism which would push or kick the tool in the direction of movement of the travelling work at the same time that the trigger circuits are energized. Such a mechanism would, however, be required only if the work is insufliciently rigid to carry the tool the relatively short dis tance.

Accordingly, a further simplified cut-off of greater versatility is provided which will obtain extremely rapid cycling severing a wide variety of shapes with blade speeds ranging, for example, from about 40 to about 200 ft. per second at impact. Such fast cycling and blade speeds are obtained without the use of drive motors, brakes, clutches, and the like found in conventional press cut-offs. There is then provided a highly simplified cutoff for tubes and the like permitting forming or production lines to operate in a faster more efficient manner.

Other modes of applying the principle of the invention may be employed, change being made as regards the details described, provided the features stated in any of the following claims or the equivalent of such be employed.

I, therefore, particularly point out and distinctly claim as my invention:

1. A flying cut-off for elongated travelling work comprising, a support frame, a cut-off mechanism including: blade guides extending transversely of such work path; a cut-off blade mounted on said guides for movement therealong; and drive means thus to move said blade; and two .pairs of spring straps one at each end thereof supporting said entire mechanism for yielding movement with respect to said frame.

2. A flying cut-off as set forth in claim 1 wherein said cut-off mechanism further includes aligned slightly spaced work gripping dies, and means to drive a cut-off blade between said dies.

3. A flying cut-off as set forth in claim 2 wherein said work gripping dies are mounted on a die support frame extending transversely of the work path, and latch means mounted on said frame operative to hold said cut-off blade on each side of such work path.

4. A flying cut-off as set forth in'claim 1 wherein said drive means comprises a pneumatic piston-cylinder as sembly, and means to supply high pressure air alternately to each side of the piston of said assembly.

5. A flying cut-off as set forth in claim 4 including means to exhaust air from the cylinder of said assembly at the central portion thereof.

6. A flying cut-ofi as set forth in claim 2 wherein said slightly spaced work gripping dies include collet assemblies, and pneumatic piston means movable axially of said collet means operative to expand and contract the same.

7. A flying cut-off as set forth in claim 6 wherein said collet means comprises a plurality of circular collet elements, and resilient compressible members circumferentially therebetween.

8. A tube cut-off comprising elongated parallel tube gripping die supports extending transversely of such tube, axially aligned annular tube gripping dies centrally disposed on said supports, guide means extending parallel to and between said supports, a cut-off blade mounted on said guide means for movement between said tube gripping dies, and blade drive means operative rapidly to drive said blade back and forth between said dies to sever a tube passing therethrough on each stroke.

9. A tube cut-off as set forth in claim 8 including shelves at the opposite ends of said die supports, and means mounting said blade drive means on one of said shelves.

10. A tube cut-off as set forth in claim 9 wherein said blade drive means comprises a piston-cylinder assembly extending parallel to said tube gripping die supports, the rod of said assembly projecting through said shelf and being connected to a blade support frame, said blade support frame being mounted on said guide means.

11. A tube cut-oif as set forth in claim 8 wherein said tube gripping dies comprise collet assemblies, and pneumatic piston means coextensive with said collet assemblies operative to open and close the same. 12. A tube cut-off as set forth in claim 11 including mteracting wedge surfaces on said collet assembly and said pneumatic piston means operative to expand and contract said collet assemblies.

13. A tube cut-off as set forth in claim 12 wherein said collet assembly includes a plurality of circular collet members having resilient compressible elements circumferentially therebetween.

14. A tube cut-off as set forth in claim 8 including latch means mounted on said die supports operative to irod said cut-off blade on each side of the path of such 15. A tube cut-off comprising a rectangular blade frame, a double edge cutting blade mounted substantially centrally in said frame, drive means for said blade frame operative to reciprocate said frame and thus said blade to sever a tube passing through said frame, and rotating releasable latch means operative to engage and catch said frame at each end of its stroke to hold said frame in a cocked position.

16. A tube cut-off as set forth in claim 15 including pin means projecting from said frame at each end thereof, said latch means including a circular rotatable latch member having a circumferential recess therein, and means mounting said latch member for rotation to engage or release said pin means in said recess.

17 A tube cut-off as set forth in claim 16 wherein said latch means includes a further circular latch member coaxially rotatable with said first circular latch member, a notch in said further latch member, and a retractible dog operative to engage said notch to hold said circular latch members against rotation.

18. A tube cut-off as set forth in claim 17 including a single acting piston-cylinder operative to retract said dog to release said latch members for rotation.

19. A tube cut-01f as set forth in claim 18 including spring means operative continuously to urge said dog into engagement with said further circular latch member. 2t). A tube cut-off as set forth in claim 1? including means to limit rotation of said circular latch members.

References Cited by the Examiner UNITED STATES PATENTS 1,318,320 10/1919 Frohn s3- 5s7 x 2,258,348 10/1941 Biggert 83578 x 2,267,543 12/1941 Watson 83-30 8 X 2,325,431 7/1943 Shippy s3 319 X 2,540,166 2/1951 Frank et al. s3 292 2,602,507 7/1952 Adams 83-587 2,648,334 8/1953 Hahn Et al. 83-639 X 2,711,764 6/1955 Slysh 146101 ANDREW R. JUHASZ, Primary Examiner.

WILLIAM W. DYER, JR., Examiner.

L. B. TAYLOR, Assistant Examiner. 

1. A FLYING CUT-OFF FOR ELONGATED TRAVELLING WORK COMPRISING, A SUPPORT FRAME, A CUT-OFF MECHANISM INCLUDING: BLADE GUIDES EXTENDING TRANSVERSELY OF SUCH WORK PATH; A CUT-OFF BLADE MOUNTED ON SAID GUIDES FOR MOVEMENT THEREALONG; AND DRIVE MEANS THUS TO MOVE SAID BLADE; AND TWO PAIRS OF SPRING STRAPS ONE AT EACH END THEREOF 